Test head positioning system and method

ABSTRACT

An apparatus for supporting a load includes pneumatic units and couplers coupled to opposite sides of the load. The couplers move the load parallel to a first axis responsive to actuation of the pneumatic units. At least one of the couplers rotate the load about a second axis orthogonal to the first axis. The load is compliant along the first axis and about the second axis At least one of the pneumatic units provides compliance along the first axis and about the second axis.

RELATED APPLICATIONS

This Application is a Divisional of application Ser. No. 11/749,988,filed May 17, 2007, which is a Divisional of application Ser. No.10/813,362, filed Mar. 30, 2004, which has now Issued as U.S. Pat. No.7,235,964, which Issued on Jun. 26, 2007, which claims the benefit of60/459,019, filed Mar. 31, 2003, all of which are incorporated byreference.

FIELD OF THE INVENTION

The present invention relates to systems for positioning andmanipulating loads, and more particularly, to systems for positioningand manipulating test heads.

BACKGROUND OF THE INVENTION

In the manufacture of integrated circuits (ICs) and other electronicdevices, testing with automatic test equipment (ATE) is performed at oneor more stages of the overall process. Special handling apparatus isused which places the device to be tested into position for testing. Insome cases, the special handling apparatus may also bring the device tobe tested to the proper temperature and/or maintain it at the propertemperature as it is being tested. The special handling apparatus is ofvarious types including “probers” for testing unpackaged devices on awafer and “device handlers” for testing packaged parts; herein,“handling apparatus” or peripheral will be used to refer to all types ofsuch peripheral apparatus. The electronic testing itself is provided bya large and expensive ATE system which includes a test head which isrequired to connect to and dock with the handling apparatus. The DeviceUnder Test (DUT) requires precision, high-speed signals for effectivetesting; accordingly, the “test electronics” within the ATE which areused to test the DUT are typically located in the test head which mustbe positioned as close as possible to the DUT. The test head isextremely heavy, and as DUTs become increasingly complex with increasingnumbers of electrical connections, the size and weight of test headshave grown from a few hundred pounds to presently as much as two orthree thousand pounds. The test head is typically connected to the ATE'sstationary mainframe by means of a cable, which provides conductivepaths for signals, grounds, and electrical power. In addition, the testhead may require coolant to be supplied to it by way of flexible tubing,which is often bundled within the cable.

In testing complex devices, hundreds or thousands of electricalconnections have to be established between the test head and the DUT.These connections are accomplished with delicate, densely spacedcontacts. In testing unpackaged devices on a wafer, the actualconnection to the DUT is typically achieved with needle-like probesmounted on a probe card. In testing packaged devices, it is typical touse a test socket mounted on a “DUT board.” In either case, the probecard or DUT board is usually fixed appropriately to the handlingapparatus, which brings each of a number of DUTs in turn into positionfor testing. In either case the probe card or DUT board also providesconnection points with which the test head can make correspondingelectrical connections. The test head is typically equipped with aninterface unit that includes contact elements to achieve the connectionswith the probe card or DUT board. Typically, the contact elements arespring loaded “pogo pins.” Overall, the contacts are very fragile anddelicate, and they must be protected from damage.

Test head manipulators may be used to maneuver the test head withrespect to the handling apparatus. Such maneuvering may be overrelatively substantial distances on the order of one meter or more. Thegoal is to be able to quickly change from one handling apparatus toanother or to move the test head away from the present handlingapparatus for service and/or for changing interface components. When thetest head is held in a position with respect to the handling apparatussuch that all of the connections between the test head and probe card orDUT board have been achieved, the test head is said to be “docked” tothe handling apparatus. In order for successful docking to occur, thetest head must be precisely positioned in six degrees of freedom withrespect to a Cartesian coordinate system. Most often, a test headmanipulator is used to maneuver the test head into a first position ofcoarse alignment within approximately a few centimeters of the dockedposition, and a “docking apparatus” is then used to achieve the finalprecise positioning. Typically, a portion of the docking apparatus isdisposed on the test head and the rest of it is disposed on the handlingapparatus. Because one test head may serve a number of handlingapparatuses, it is usually preferred to put the more expensive portionsof the docking apparatus on the test head. The docking apparatus mayinclude an actuator mechanism which draws the two segments of the docktogether, thus docking the test head; this is referred to as “actuatordriven” docking. The docking apparatus, or “dock” has numerous importantfunctions, including: (1) alignment of the test head with the handlingapparatus, (2) pulling together, and later separating, the test head andthe handling apparatus, (3) providing pre-alignment protection forelectrical contacts, and (4) latching or holding the test head and thehandling apparatus together.

According to the in TEST Handbook (5^(th) Edition © 1996, in TESTCorporation), “Test head positioning” refers to the easy movement of atest head to a handling apparatus combined with the precise alignment tothe handling apparatus required for successful docking and undocking. Atest head manipulator may also be referred to as a test head positioner.A test head manipulator combined with an appropriate docking meansperforms test head positioning. This technology is described, forexample, in the aforementioned in TEST Handbook. This technology is alsodescribed, for example, in U.S. Pat. Nos. 5,608,334, 5,450,766,5,030,869, 4,893,074, 4,715,574, and 4,589,815, which are allincorporated by reference for their teachings in the field of test headpositioning systems. The foregoing patents relate primarily to actuatordriven docking. Test head positioning systems are also known where asingle apparatus provides both relatively large distance maneuvering ofthe test head and final precise docking. For example, U.S. Pat. No.6,057,695, Holt et al., and U.S. Pat. Nos. 5,900,737 and 5,600,258,Graham et al., which are all incorporated by reference, describe apositioning system where docking is “manipulator driven” rather thanactuator driven. However, actuator driven systems are the most widelyused, and the present invention is directed towards them.

In the typical actuator driven positioning system, an operator controlsthe movement of the manipulator to maneuver the test head from onelocation to another. This may be accomplished manually by the operatorexerting force directly on the test head in systems where the test headis fully balanced in its motion axes, or it may be accomplished throughthe use of actuators directly controlled by the operator. In severalcontemporary systems, the test head is maneuvered by a combination ofdirect manual force in some axes and by actuators in other axes.

In order to dock the test head with the handling apparatus, the operatormust first maneuver the test head to a “ready to dock” position, whichis close to and in approximate alignment with its final docked position.The test head is further maneuvered until it is in a “ready to actuate”position where the docking actuator can take over control of the testhead's motion. The actuator can then draw the test head into its final,fully docked position. In doing so, various alignment features providefinal alignment of the test head. A dock may use two or more sets ofalignment features of different types to provide different stages ofalignment, from initial to final. It is generally preferred that thetest head be aligned in five degrees of freedom before the fragileelectrical contacts make mechanical contact. The test head may then beurged along a straight line, which corresponds to the sixth degree offreedom, that is normal to the plane of the interface (typically theplane of the probe card or DUT board); and the contacts will makeconnection without any sideways scrubbing or forces which can bedamaging to them.

As the docking actuator is operating, the test head is typically free tomove compliantly in several if not all of its axes to allow finalalignment and positioning. For manipulator axes which are appropriatelybalanced and not actuator driven, this is not a problem. However,actuator driven axes generally require that compliance mechanisms bebuilt into them. Some typical examples are described in U.S. Pat. Nos.5,931,048 to Slocum et al and 5,949,002 to Alden. Often compliancemechanisms, particularly for non-horizontal unbalanced axes, involvespring-like mechanisms, which in addition to compliance add a certainamount of resilience or “bounce back.” Further, the cable connecting thetest head with the ATE mainframe is also resilient. As the operator isattempting to maneuver the test head into approximate alignment and intoa position where it can be captured by the docking mechanism, he or shemust overcome the resilience of the system, which can often be difficultin the case of very large and heavy test heads. Also, if the operatorreleases the force applied to the test head before the docking mechanismis appropriately engaged, the resilience of the compliance mechanismsmay cause the test head to move away from the dock. This is sometimesreferred to as a bounce back effect.

U.S. Pat. No. 4,589,815, to Smith, discloses a prior art dockingmechanism. The docking mechanism illustrated in FIGS. 5A, 5B, and 5C ofthe '815 patent uses two guide pin and hole combinations to providefinal alignment and two circular cams. When the cams are rotated byhandles attached to them, the two halves of the dock are pulled togetherwith the guide pins becoming fully inserted into their mating holes. Awire cable links the two cams so that they rotate in synchronism. Thecable arrangement enables the dock to be operated by applying force tojust one or the other of the two handles. The handles are accordinglythe docking actuator in this case.

The basic idea of the '815 dock has evolved as test heads have becomelarger into docks having three or four sets of guide pins and circularcams interconnected by cables. FIGS. 37 a, 37 b, 37 c, and 37 d of thepresent application illustrate a prior art dock having four guide-pinand hole combinations and four circular cams, which is described in moredetail later. Although such four point docks have been constructedhaving an actuator handle attached to each of the four cams, the dockshown incorporates a single actuator handle that operates a cabledriver. When the cable driver is rotated by the handle, the cable ismoved so that the four cams rotate in a synchronized fashion. Thisarrangement places a single actuator handle in a convenient location forthe operator. Also, greater mechanical advantage can be achieved byappropriately adjusting the ratio of the diameters of the cams to thediameter of the cable driver.

The docks described in U.S. Pat. Nos. 5,654,631 and 5,744,974 utilizeguide pins and holes to align the two halves. However, the docks areactuated by vacuum devices, which urge the two halves together whenvacuum is applied. The two halves remain locked together so long as thevacuum is maintained. However, the amount of force that can be generatedby a vacuum device is limited to the atmospheric air pressure multipliedby the effective area. Thus, such docks are limited in theirapplication.

Selected details of the construction and operation of the prior art dockillustrated in FIGS. 37 a through 37 d are herein described. Thisdescription includes aspects from an earlier docking apparatus describedin U.S. Pat. No. 4,589,815, which is incorporated by reference.

FIG. 37 a shows in perspective a test head 2100 held in a cradle 2190,which is in turn supported by a test head manipulator (not shown). Alsoshown is a cut away segment of a peripheral apparatus 2108 to which thetest head 2100 may be docked. FIG. 37 b shows peripheral handler 108 insomewhat larger scale and greater detail. (In this particular examplethe handler apparatus is a packaged device handler, and the test head isdocked to it from below.) Briefly looking ahead to the sectional view inFIG. 37 c, it is seen that the test head 2100 has electrical interface2126, and the handler apparatus 2108 has a corresponding electricalinterface 2128. Electrical interfaces 2126 and 2128 typically havehundreds or thousands of tiny, fragile electrical contacts (not shown)that must be precisely engaged in a manner to provide reliablecorresponding individual electrical connections when the test head isfinally docked. As is shown in this exemplary case, the lower surface ofhandler apparatus 2108 contains the handler electrical interface 2128,and the test head 2100 is docked with a generally upward motion frombelow. Other orientations are possible and known including, but notlimited to: docking to a top surface with a downward motion, to avertical plane surface with horizontal motion, and to a plane that is atan angle to both the horizontal and vertical.

Returning to FIGS. 37 a and 37 b, the complete four point dockingapparatus is shown; portions of it are attached either to the handlerapparatus 2108 or to the test head 2100. Attached to test head 2100 isfaceplate 2106. Four guide pins 2112 are attached to and located nearthe four corners of faceplate 106. Face plate 106 has a central openingand is attached to test head 100 so that the test head electricalinterface 2126 (not shown in FIGS. 37 a and 37 b) projects through theopening and guide pins 2112 define an approximate rectangle that has anapproximate common center with electrical interface 2126.

Gusset plate 2114 is attached to the lower surface of the handlerapparatus 2108. Gusset plate 2114 has a central opening and is attachedto handler apparatus 2108 so that the handler electrical interface 2128projects through the opening. Four gussets 2116 are attached to gussetplate 2114, one located near each of its four corners. Each gusset 2116has a guide pin hole or receptacle 2112 a bored in it. Each guide pinhole 2112 a corresponds to a respective guide pin 2112. These arearranged so that when the test head is fully docked, each guide pin 2112will be fully inserted into its respective guide pin hole 2112 a. Thefit of each guide pin 2112 in its corresponding hole 2112 a is a closefit. Thus, the guide pins 2112 and guide pin holes 2112 a providealignment between the test head 2100 and the handler apparatus 2108.

Four docking cams 2110 are rotatably attached to the face plate 2106.Cams 2110 are circular and are similar to those described in the '815patent. In particular each has a side helical groove 2129 around itscircumference with an upper cutout 2125 on the upper face. Each dockingcam 2110 is located in proximity to a respective guide pin 2112 suchthat it is generally centered on a line extending approximately from thecenter of the test head electrical interface 2126 through the respectiveguide pin 2112 such that guide pin 2112 lies between cam 2110 and thetest head electrical interface 2126. The gussets 2116 and the corners ofthe gusset plate 2114 have circular cutouts such that when the guidepins 2112 are fully inserted into guide pin holes 2112 a in the gussets,the circumference of each cam 2110 is adjacent to and concentric withthe circular cutout in its respective gusset 2116. This arrangementprovides an initial course alignment between the docking components asthe test head 2100 is first maneuvered into position for docking withhandler apparatus 2108. Initial coarse alignment may also be provided bythe tapered ends of guide pins 2112 entering their respectivereceptacles 2112 a. The gussets 2116, cams 2110, and guide pins 2112 arearranged so that handler electrical interface 2128 is kept separatedfrom test head electrical interface 2126 (not shown in FIGS. 37A and37B) until the guide pins 2112 are actually received in their respectiveguide pin holes 2112 a. Thus, pre-alignment protection is provided tothe electrical contacts.

Thus, two sets of alignment features are provided, namely: (1) the fitof gussets 2116 with respect to cams 2110, and (2) the guide pin 2112and receptacle 2112 a combinations.

A circular cable driver 2132 with an attached docking handle 2135 isalso rotatably attached to face plate 2106. Docking cable 2115 isattached to each of the cams 2110, and to cable driver 2132. Pulleys2137 appropriately direct the path of the cable to and from cable driver2132. Cable driver 132 can be rotated by means of applying force tohandle 2135. As cable driver 2132 rotates it transfers force to cable2115 which in turn causes cams 2110 to rotate in synchronism.

Extending from the circular cutout of each gusset 2116 is a cam follower2110 a. Cam follower 2110 a fits into the upper cutout on the upper faceof its respective cam 2110. FIG. 37 c shows in cross section one stagein the process of docking test head 2100 with handler apparatus 2108.Here guide pins 2112 are partially inserted into guide pin holes 2112 ain gussets 2116. It is noted that in this exemplary case, guide pins2112 are tapered near their distal ends and are of constant diameternearer to their point of attachment to face plate 2106. In FIG. 37 cguide pins 2112 have been inserted into guide pin holes 2112 a to apoint where the region of constant diameter is just entering the guidepin holes 2112 a. Also in FIG. 37 c, each cam follower 2110 a has beeninserted into the upper cutout 2125 on the upper face of its respectivecam 2110 to a depth where it is at the uppermost end of the helical camgroove 2129. In this configuration, the dock is ready to be actuated byapplying force to the handle 2135 (not shown in FIG. 37 c) and rotatingthe cams 2110. Accordingly, this configuration may be referred to as the“ready to actuate” position. It is important to note that in thisposition, alignment in five degrees of freedom has been achieved. Inparticular, if the plane of the handler apparatus electrical interface2126 is the X-Y plane of three dimensional interface, guide pins 2112having their full diameter inserted into receptacles has established X,Y, and theta Z alignment. Furthermore, the insertion of cam followers2110 a fully into all cut outs 2125 has established planarizationbetween the handler apparatus electrical interface 2126 and the testhead electrical interface 2128.

FIG. 37 d shows in cross section the result of fully rotating cams 2110.The test head 2100 is now “fully docked” with handler apparatus 2108. Itis seen that cams 2110 have been rotated and have caused cam followers2110 a to follow the helical grooves 2129 to a point in closer proximityto faceplate 2106. In addition, guide pins 2112 are fully inserted intotheir respective guide pin holes 2112 a. It is observed that thecloseness of the fit between the constant diameter region of guide pins2112 and the sides of the respective guide pin holes 2112 a determinesthe final alignment between the handler electrical interface 2128 andthe test head electrical interface 2126. Accordingly, a close fit isgenerally required to provide repeatability of docked position withinthree to seven thousandths of an inch. Furthermore, the guide pins 2112must be precisely placed on face plate 2106 with respect to the gussetsonce gusset plate 2114 has been attached to handler apparatus 2108. Tofacilitate this, the guide pins 2112 may be attached in a manner thatallows their position to be adjusted. A manner of doing this which iswidely practiced is described in the '815 patent.

In light of the foregoing discussion, it is now appropriate to morefully discuss the docking process and define certain terms. The purposeof docking is to precisely mate the test head electrical interface 2126with the handler apparatus electrical interface 2128. Each electricalinterface 2126 and 2128 defines a plane, which is typically, but notnecessarily, nominally parallel with the distal ends of the electricalcontacts. When docked these two planes must be parallel with oneanother. In order to prevent damage to the electrical contacts, it ispreferred to first align the two interfaces 2126 and 2128 in fivedegrees of freedom prior to allowing the electrical contacts to comeinto mechanical contact with one another. If in the docked position thedefined planes of the interfaces are parallel with the X-Y plane of athree dimensional Cartesian coordinate system, alignment must occur inthe X and Y axes and rotation about the Z axis (Theta Z), which isperpendicular to the X-Y plane, in order for the respective contacts toline up with one another. Additionally, the two planes are made parallelby rotational motions about the X and Y axes. The process of making thetwo electrical interface planes parallel with one another is called“planarization” of the interfaces; and when it has been accomplished,the interfaces are said to be “planarized” or “co-planar.” Onceplanarized and aligned in X, Y and Theta Z, docking proceeds by causingmotion in the Z direction perpendicular to the plane of the handlerelectrical interface 2128. In the process of docking, test head 2100 isfirst maneuvered into proximity of the handler 2108. Further maneuveringbrings the circular cutouts of the gussets 2116 into a first alignmentwith the cams 2110. This position, or one just prior to it, may beconsidered to be a “ready to dock” position. More generally, “ready todock” refers to a position where some first coarse alignment means isapproximately in position to be engaged. At this stage and dependingupon design details, the distal end of the guide pins are ready to entertheir respective guide receptacles. Still further maneuvering will bringthe test head to a “ready to actuate position,” which was definedpreviously in terms of FIGS. 37A through 37D. More generally, “ready toactuate” refers to a position where a test head has achieved a positionwhere a docking apparatus may be actuated. At the ready to actuateposition, approximate planarization and alignment in X, Y and Theta Zhave been achieved. As the dock is actuated and the guide pins 2112become more fully inserted into their respective guide-pin holes 2112 a,alignment and planarization become more precise. It is noted that inmanipulator driven docking, as described in the '258 and '737 patents,sensors detect the equivalent of a ready to actuate position in order tochange from a coarse positioning mode to a fine positioning mode. Thus,to one of ordinary skill in the art, sensing a ready to actuate positionin an actuator driven dock would be a natural extension (intuitive andobvious) of what is taught and disclosed by the '258 and '737 patents.

Docks of the type described above have been used successfully with testheads weighing up to and over one thousand pounds. However, as testheads have become even larger and as the number of contacts hasincreased, a number of problems have become apparent. First, the forcerequired to engage the contacts increases as the number of contactsincreases. Typically a few ounces per contact is required; thus dockinga test head having 1000 or more contacts requires in excess of 50 or 100kilograms for this purpose. With test heads occupying a volume of acubic yard or more it becomes increasingly difficult for the operatorsto observe all of the gussets and cams to determine when the test headis in a ready to dock and the ready to actuate positions. Also due tothe resiliency of the compliance mechanisms and cable in the test headmanipulator, the bounce back effect has made it difficult to maintainthe test head in the ready to actuate position while simultaneouslyinitiating the actuation. A further difficulty that arises from theincreased amount of force to be overcome by the actuation mechanism isthat the cam motion can become unsynchronized due to the stretching ofthe cable. A similar problem of mechanism distortion is known in docksusing solid links and bell cranks.

Docking apparatus such as described above may be characterized by thenumber of guide pins and receptacles used. The apparatus described inthe '815 patent is characterized as a two-point dock, and the apparatusshown in FIGS. 37A through 37D is known as a four point dock. Threepoint docks following the same general principles are also known and incommon use, and the present invention will be described in terms of athree-point configuration. However, this does not limit its applicationto other configurations.

SUMMARY OF THE INVENTION

An apparatus for supporting a load includes pneumatic units and couplerscoupled to opposite sides of the load. The couplers move the loadparallel to a first axis responsive to actuation of the pneumatic units.At least one of the couplers rotates the load about a second axisorthogonal to the first axis. The load is compliant along the first axisand about the second axis At least one of the pneumatic units providescompliance along the first axis and about the second axis.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view which shows a positioner system accordingto an exemplary embodiment of the present invention.

FIG. 2 is an exploded view of the positioner system shown in FIG. 1.

FIG. 3 is a further exploded view of the positioner system shown in FIG.1.

FIG. 4 is a perspective view of the base of the positioner system shownin FIG. 1.

FIG. 5 is a further perspective view showing an enlarged portion of thebase illustrated in FIG. 4.

FIG. 6 is an exploded view of the in-out unit of the exemplarypositioner system.

FIG. 7 is a further exploded view of the in-out unit shown in FIG. 6.

FIG. 8 is an exploded view of the side-to-side unit of the exemplarypositioner system.

FIG. 9 is a partially exploded view of the side-to-side unit shown inFIG. 8, but from a different perspective than that shown in FIG. 8.

FIG. 10 is a further perspective view of the side-to-side unit.

FIG. 11 a is an exploded view of the swing unit of the exemplarypositioner system.

FIG. 11 b is a perspective view of the swing unit with belts shown.

FIG. 12 is a partially exploded view of the swing unit shown in FIG. 11a, but from a different perspective.

FIG. 13 is an exploded view of a main arm of the exemplary positionersystem.

FIG. 14 a is a partially exploded view of the main arm unit, but from adifferent perspective than that shown in FIG. 13.

FIG. 14 b is a schematic diagram illustrating a pressure regulationsystem used with the pneumatic cylinders of FIGS. 13 and 14 a.

FIG. 15 is a perspective view of a vernier arm of the exemplarypositioner system.

FIG. 16 is a perspective view of a further vernier arm of the exemplarypositioner system.

FIG. 17 is an exploded view of the tumble drive unit of the exemplarypositioner system.

FIG. 18 is a further exploded view of the tumble drive unit, but from adifferent perspective than that shown in FIG. 17.

FIG. 19 is a further exploded view of the tumble drive unit, but from adifferent perspective than that shown in either of FIGS. 17 and 18.

FIG. 20 is an exploded perspective view of a gear, bushing and axlewhich are used with the tumble drive unit shown in FIGS. 17, 18 and 19.

FIG. 21 is perspective view of the tumble drive unit of FIGS. 17, 18 and19 with the drive gear, bushing and axle installed.

FIGS. 22 a and b are perspective views of a tumble pivot unit of theexemplary positioner system.

FIG. 23 is a perspective drawing illustrating the application of dockingmodule mechanisms in accordance with an exemplary embodiment of thepresent invention.

FIG. 24 is a perspective drawing of a docking pin in accordance with anexemplary embodiment of the present invention.

FIGS. 25 a and b are cut-away side views of a docking module mechanism.

FIG. 26 is an exploded perspective view of a docking module mechanism inaccordance with an exemplary embodiment of the present invention.

FIG. 27 is a perspective view of a pin receptacle in accordance with anexemplary embodiment of the present invention.

FIG. 28 is a perspective view of a pin detector in accordance with anexemplary embodiment of the present invention.

FIG. 29 is a perspective view of a pin detector with the detector tabremoved in accordance with an exemplary embodiment of the presentinvention.

FIG. 30 is a perspective view of a detector tab in accordance with anexemplary embodiment of the present invention.

FIG. 31 is a perspective view of a piston unit in accordance with anexemplary embodiment of the present invention.

FIG. 32 is a perspective view of an arm in accordance with an exemplaryembodiment of the present invention.

FIGS. 33 through 36 is a sequence of side views of the docking modulemechanism which shows a method of docking in accordance with anexemplary embodiment of the present invention.

FIG. 37 is a flow chart diagram which describes exemplary steps fordocking a test head with a peripheral.

FIG. 38 a is a perspective view of a prior art docking apparatus.

FIG. 38 b is a perspective view of the portion of a prior art dockingapparatus that is attached to a peripheral apparatus.

FIG. 38 c is a sectional view of the prior art docking apparatus in theready to actuate position.

FIG. 38 d is a sectional view of the prior art docking apparatus in thefully docked position.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 is a perspective drawing of a positioner system 10 according toan exemplary embodiment of the present invention. A positioner system 10is used for holding and moving a heavy load such as a test head which ismore fully described in U.S. Pat. No. 4,527,942, which is incorporatedby reference. As shown in that patent, FIG. 6, six degrees of motionfreedom are defined. The positioner system 10 in accordance with anexemplary embodiment of the present invention accomplishes these sixdegrees of motion freedom. FIG. 2 is an exploded view of the positionersystem shown in FIG. 1. As shown, at the bottom of FIG. 2, base 50 isincluded. In-out unit 100 rides on base 50, which rests upon the floor.As is implied by its name, in-out unit 100 is capable of sliding,parallel with the floor along the Z axis, in an in direction (i.e. awayfrom the rear face of in-out unit 100 and towards its opening), and inan out direction (i.e., towards the rear face of in-out unit 100). Thein direction is usually taken to be the direction towards a dockedposition with a peripheral, and the out direction as away from theperipheral.

Side-to-side unit 200 slides along the X axis on in-out unit 100, alsoparallel with the floor. The motion of side-to-side unit 200 isorthogonal to that of in-out unit 100.

Swing unit 300 is situated on side-to-side unit 200. Swing unit 300pivots about a Y axis which is mutually orthogonal to the axes alongwhich side-to-side unit 200 moves and in-out unit 100 moves. This isalso referred to as twisting, swing, or yaw motion. Main arm units 400,500 slide along a Y axis upward and downward along linear rails whichare vertically disposed in swing unit 300. To provide vernier Y motion,vernier arm 600 is able to move upward and downward along a linear guiderail vertically disposed in main arm 400. Furthermore, vernier arm 700moves upward and downward along a linear rail vertically disposed withrelationship to main arm 500. Vernier Y motion is a relatively smallamount of motion (e.g. one or two inches) which is provided for finalfine-tuning of the Y position. This motion may be a floating motionwhich is accomplished by air pressure. Tumble pivot unit 900 is coupledto vernier arm 600. Tumble drive unit 800 is coupled to vernier arm 700.The test head rotates (i.e. with tumbling or pitch motion) about an Xaxis which extends through tumble drive unit 800 and tumble pivot unit900. This axis may be arranged so that it passes through the center ofgravity of the load in order to allow the test head to pivot with aminimal amount of applied force.

FIG. 3 is a further perspective view of the various components whichcomprise positioner system 10.

Base 50 is more clearly described with reference to FIG. 4. As shown,base 50 includes linear guide rail 52 a and linear guide rail 52 b (notvisible in FIG. 4). In-out drive motor 65 and in-out position encoder 70are included in the base assembly. Motor 65 may include appropriatespeed reduction gears. Motor 65 may also include a brake unit to lock itin a stopped position when desired. As is more clearly shown by FIG. 5,motor pulleys 66 are attached to the shaft of in-out motor 65 in aconventional manner. Position encoder 70 (not visible in FIG. 5) iscoupled to bracket 80 which in turn is coupled to base 50. Encoderpulley 71 is attached to the shaft of encoder 70 in a conventionalmanner.

Two timing belts (not shown) are also included. The first belt couplesone of motor pulleys 66 to pulley 60 so that pulley 60 rotates as themotor rotates. This first belt is disposed generally parallel to linearguide rails 52 a,b. The second belt couples the other of the motorpulleys 66 to encoder pulley 71 so that the encoder rotates as the motorrotates.

The details of in-out unit 100 are more clearly shown with reference toFIGS. 6 and 7. Linear guide bearings 102, 104, 106 and 108 are attachedto the underside of in-out substrate 110. Linear guide bearings 102, 104move along linear guide rail 52 a. Furthermore, linear guide bearings106, 108 slide along linear guide rail 52 b.

In-out unit 100 is able to move in an in-and-out direction when motor 65is actuated. More specifically, when motor 65 is actuated, the belts(not shown in FIG. 4 or in FIG. 5) start to move. The belt couplingmotor pulley 66 to pulley 60 is attached to in-out unit 100 at aconvenient point. Thus, as the belt moves, in-out unit 100 is driven inan inwards or outwards direction according to the direction of rotationof motor 65. Should motor 65 include a brake unit, it may be used tolock the in-out unit in a fixed position relative to base 50 whendesired.

Also as shown in FIGS. 6 and 7, linear guide rails 112, 114 are affixedto the top of in-out substrate 110 so as to be orthogonal to linearguide rails 52 a,b attached to base 50. Side-to-side drive motor 120 isalso included. Adjacent to motor 120 is motor bracket 125, and pulley142. Motor 120 may include appropriate speed reduction gears. Motor 120may also include a brake unit to lock it in a stopped position whendesired. Side-to-side position encoder 130 is also included. Pulley 144is affixed to position encoder 130. A belt (not shown) couples pulley142 to pulley 144. The belt is generally disposed parallel to rails 112and 114. Thus, encoder 130 will be rotated as motor 120 rotates. Covers152 and 154 are also included.

Turning now to FIGS. 8, 9 and 10, the features of side-to-side unit 200will now be described. As is more clearly shown in FIG. 10, which showsits underside, side-to-side unit includes linear guide bearings 210,212, 214 and 216. Linear guide bearings 214, 216 slide along linearguide rail 114 while linear guide bearings 210, 212 slide along linearrail 112. Recall that guide rails 112 and 114 are respectively attachedto in-out substrate 110. Side-to-side substrate 220 includes an openingthrough which swing plate mounting assembly 260 is situated. Swing platemounting assembly 260 includes a drive link 260 a along with a pluralityof seals and rings. Swing drive motor 230 is included, which may includeappropriate speed reduction gears. Motor 230 may also include a brakeunit to lock it in a stopped position when desired. Drive shaft 250 iscoupled to pulley 254. Pulley 254 is coupled to pulley 256 by means of abelt (not shown). Pulley 256 is attached to position encoder 240. As analternative position encoder 240 could be coupled to drive shaft 250 bymeans of gears.

The rotation axis of drive shaft 250 is generally horizontal and atright angles to the generally vertical rotation axis of swing platemounting assembly 260. The two are engaged with one another throughappropriate gearing, such as a spiral gear drive or a worm gear drive,so that as shaft 250 is rotated, mounting assembly 260 is caused torotate at right angles to it. Compliance may be achieved by a slightseparation between drive shaft 250 and swing plate mounting assembly260.

Movement of side-to-side unit 200 relative to base 100 is now described.The belt, which couples pulleys 142 and 144 (FIG. 6), may be attached toside-to-side substrate 220 at a convenient point. Thus as side-to-sidedrive motor 120 is operated the belt coupling pulleys 142 and 144 moves,causing side-to-side unit 200 to accordingly move. If motor 120 isequipped with a brake unit, then the brake unit may be used to lock theside-to-side unit 200 in position relative to in-out unit 100 whendesired.

Swing unit 300 is shown in FIGS. 11 a, 11 b, and 12. Swing unit opening302 engages swing plate mounting assembly 260 shown in FIGS. 8, 9 and10. Thus, as swing plate mounting assembly 260 rotates, swing unit 300rotates in conjunction therewith. More specifically, as motor 230 spins,drive shaft 250 also spins. Swing plate mounting assembly 260 rotatesbecause it is turned by drive shaft 250, as previously described. Thus,as swing plate mounting assembly rotates, swing unit 300 also rotates.If motor 230 is equipped with a brake unit, then the brake unit may beused to lock the swing unit 300 in position relative to side-to-sideunit 200 when desired.

Referring to FIGS. 11 a, 11 b, and 12, swing unit 300 includes swingunit substrate 305. Columns 315 a,b and side panels 310 a,b are attachedto swing unit substrate 305. Linear guide rails 320 a,b are attached tocolumns 315 a,b respectively and are essentially parallel, defining avertical plane. Lead screws 325 a,b are mounted to swing unit substrate305 in the positions shown in front of columns 315 a,b respectively.Pulleys 326 a and 326 b are attached to the ends of screws 325 a and 325b respectively. Pulleys 326 a,b are located underneath substrate 305 andscrews 325 a,b extend upwards through holes in substrate 305.Appropriate bearings are used in a conventional fashion to secure screws325 a,b to substrate 305 in a secure manner which allows them to freelyrotate. Screws 325 a,b may be ball screws. However, as will bediscussed, screws 325 a,b ultimately support the heavy load, and thethread style and pitch must be selected to prevent back-driving in casedrive power is lost.

Also included are vertical drive motor 330, which may includeappropriate speed reduction gears, and vertical position encoder 340.Motor 330 may also be equipped with a brake to prevent rotation when itis not in operation. Motor pulley 331 is attached to the shaft of motor330, and encoder pulley 341 is attached to encoder 340. A hand crank 350is also included which is attached to crank pulley 351. Pulleys 331,341, and 351 are located underneath substrate 305. Idler pulley 371 isattached on the underside of substrate 305.

A set of three belts 361, 362, 363 interconnect pulleys 326 a,b, 331,341, 351, 371. First belt 361 couples motor pulley 331 to lead screwpulley 326 b. Second belt 362 couples screw pulley 326 b with encoderpulley 341 and crank pulley 351. Idler 371 tensions and guides secondbelt 362. Finally, third belt 363 couples lead screw pulley 326 a withcrank pulley 351. Thusly, in operation, rotation of motor 330 shaftcauses the two lead screws 326 a,b and encoder 340 to rotate. Hand crank350 rotates as well. For manual operation, hand crank 350 may be used toturn the two lead screws 325 a,b. The two screws 325 a,b are identicalin thread type and pitch; they are driven in synchronism by either motor330 or hand crank 350.

As shown in FIG. 2, main arms 400, 500 ride along linear guide rails 320b,a respectively. While there are two main arms, namely main arm 400 andmain arm 500, the following description will relate to main arm 400. Thedescription of main arm 500 is identical to that of main arm 400 expectfor its position, and the linear guide rail and screw which it engages.

As shown in FIGS. 13 and 14 a, main arm 400 includes linear guidebearings 410, 420. Linear guide bearings 410, 420 ride along linearguide rail 320 b (shown in FIG. 12). A longitudinal bore 462, having adiameter slightly greater than that of screws 325 a,b, extends thelength of main arm 400. The entrance area of bore 462 is appropriatelyenlarged and shaped to receive nut 460, which is rigidly attached tomain arm 400. Nut 460 is threaded so that it can receive screw 325 b.Thus, screw 325 b is threaded through nut 460 and extends into bore 462.

Thus, as screw 325 b rotates, nut 460 rides up and down along screw 325b. In this way, main arm 400 is able to move upwards and downwards. Mainarm 400 includes pneumatic cylinder 440, linear guide rail 470,retaining member 450 to hold pneumatic cylinder in place and top 480.

Because screws 325 a,b are rotated in synchronism and have the samethread, the two main arms 400, 500 move up and down in synchronism. Asthe main arms 400, 500 are accordingly raised and lowered, verticalposition encoder 340 records their vertical position. Should motor 330be equipped with a brake, it may be used to lock the screws 325 a,b andprevent them from turning. Even if this is the case, it is stillpreferable that screws 325 a,b be non-backdrivable by the heavy load forsafety reasons.

Vernier arms 600 & 700 are similar in operation. Vernier arm 600, shownin FIG. 15, moves along linear guide rail 470. For this purpose, vernierarm 600 includes linear guide bearings 610, 620. Furthermore, vernierarm 700 is shown in FIG. 16. Vernier arm 700 moves along linear guiderail 570. For this purpose, linear guide bearings 710, 720 are included.Vernier arms 600, 700 are supported by pneumatic cylinders 440, 540respectively. Pneumatic piston shafts 441, 541 directly engage thebottoms of vernier arms 600, 700. As seen in FIGS. 1 and 2 (and to bedescribed in more detail later) tumble pivot unit 900 is attached to andsupported by vernier arm 600, and tumble drive unit 800 is attached toand supported by vernier arm 700. A horizontal “tumble” axis is definedbetween pivot unit 900 and drive unit 800. The test head load isrotatably mounted to pivot unit 900 and drive unit 800 at essentiallythe two points where the tumble axis passes through them. The tumbleaxis is preferably parallel to the plane defined by the two parallelrails 320 a,b.

Thus the test head load is supported by tumble pivot unit 900 and tumbledrive unit 800, which are in turn respectively supported by pneumaticcylinders 440 and 540. Pneumatic cylinders 440 and 540 beingrespectively coupled to main arms 400 and 500. The vertical range ofmotion of either vernier vertical arm 600, 700 is approximately ±25 mmwith respect to its associated main arm 400, 500.

A purpose of the vertical vernier arms 600, 700 is to provide compliantmotion, in two degrees of freedom, of the test head during docking. Eachpneumatic cylinder 440, 540 is provided with a regulated supply of air.That is, two regulators are provided: one for cylinder 440 and thesecond for cylinder 540. A common high pressure air supply may beprovided to both regulators. The pressure in each cylinder 440, 540 maythus be independently regulated. By adjusting the air pressure in thecylinders 440,540 the test head may be moved upwards or downwards withrespect to main arms 400,500. In this manner, the test head may beapproximately centered within its range of vertical vernier motion. Theposition of the test head within the vertical vernier range may bemaintained in the absence of any external forces by maintaining aconstant pressures within the cylinders 440, 540 sufficient to offsetthe downwards force exerted on the respective piston shafts 441, 541 bythe test head load. Because each cylinder is independently regulated,the pressures in the two cylinders need not be equal. This permits theload to have a center of gravity which, typically, is not necessarilycentered between the two columns. If an external force pushes downwardson the test head, the pressure in cylinders 440, 540 tries to increase.The regulators accordingly bleed off some air to maintain a constantpressure. The test head accordingly moves down. Similarly, if an upwardsforce is applied, the cylinder pressures try to decrease, the regulatorssupply more air to maintain a constant pressure, and the test head movesup. Thus, the test head is maintained in a substantially weightless orfloating condition. Furthermore, if an external torque is exerted on thetest head attempting, for example, to move one side up and the otherside down, the pneumatic cylinders facilitate this motion as theregulators supply more air to one cylinder while bleeding air from theother cylinder. Thus, this arrangement facilitates compliant motion ofthe test head in two degrees of freedom: vertical (along a Y axis) androtational (theta-Z) motion about an axis which is perpendicular to theplane defined by linear rails 320 a,b and, consequently, parallel with aZ axis. Furthermore, the rotational compliance may be about an axiswhich does not necessarily pass through the center of gravity of theload; the substantially weightless or floating condition with respect tothis motion does not depend upon the location of the axis of rotation asit does in prior art systems.

In order to carry out the vertical and rotational compliant motionsprovided by pneumatic cylinders 440 and 540 a pressure regulationapparatus is provided, which is shown schematically in FIG. 14 b.Although the present description and embodiment uses air as the workingfluid, other working fluids may be substituted within the spirit of theinvention. Two, identical pressure regulation systems R6 are provided,one for each pneumatic cylinder 440, 540, so that the pressure withineach cylinder may be independently controlled. Pressurized air is inputto both regulation systems R6 from a common source R7 as is commonlyavailable in most testing or other industrial facilities.

Each pressure regulation system R6 includes a pressure regulator R8,which may be adjusted to provide sufficient pressure to support the loadon the corresponding cylinder 440. The pressure provided by regulator R8first flows through electromagnetically controlled valve R9, which isswitched to allow flow through to cylinder 440 in the activated state.Valve R9 has a spring return so that in the event of a power failure,valve R9 is returned to a position in which the return flow fromcylinder 440 is blocked, thus preventing sudden pressure loss at theload.

Regulator system R6 seeks to maintain constant pressure at its output byallowing more air to flow from source R7 in the event of a pressure dropat the load, and by releasing air in the event of a pressure rise at theload. Regulator R8 provides such steady state control. Provided parallelto valve R9 is one-way restrictor R0, which facilitates adequatetransient response in flow to small movements imposed on the load byexternal forces for positioning purposes. The two lines from valve R9and restrictor R0 are brought together to form fluid line 25 which feedsinto cylinder 440.

If one side of the load should now be manually raised with respect toits corresponding cylinder 440, then the pressure in cylinder 440 isreduced in accordance with the lifting force. Pressure regulation systemR6 recognizes the drop in pressure and increases the fluid pressure byfeeding additional fluid into cylinder 440 until the original targetpressure is reached. Alternatively, if one side of the load is presseddownwards with respect to its cylinder 440, the pressure in cylinder 440increases. Pressure regulation system R6 recognizes this pressureincrease and diverts fluid out of cylinder 440 until the original targetpressure is reached again.

Theta-Z (or roll) motion may be accomplished by an appropriate amount offlexibility where the test head (or its cradle) is coupled to thepositioner system. For example, loose fitting balls and sockets or anappropriate sliding or flexing arrangement may be used for thiscoupling.

Turning now to consideration of tumble motion, tumble drive unit 800 iscoupled to vernier arm 700. Thus, as vernier arm 700 moves upwards anddownwards along linear guide rail 320 a, tumble drive unit also moveswith vernier arm unit 700.

Tumble drive unit 800 is shown with reference to FIGS. 17, 18, 19, 20and 21. Tumble drive unit 800 includes tumble drive motor 810 and tumbleposition encoder 820. Motor 810 may include speed reduction gears. Motor810 may also include a brake unit if desired. Motor 810 is coupled topulley 876. Drive shaft 830 is coupled to pulley 875. Pulleys 875 and876 are coupled with a belt (not shown). Thus, as the shaft of motor 810rotates, drive shaft 830 also rotates. As an alternative implementation,gears could be used in place of the pulleys 875, 876 and belt. Driveshaft 830 includes worm drive (or the like) gear teeth 889 (not shown)which engage drive gear 880 (not shown in FIGS. 17, 18 and 19, describedbelow). Drive shaft 830 is coupled to position encoder 820 via pulleys872, 871 and a belt (not shown). Thus, as drive shaft 830 rotates, theshaft of position encoder 820 also rotates. As an alternativeimplementation, gears could be used in place of the pulleys 871, 872 andbelt.

FIG. 20 shows an exploded view of drive gear and axle assembly 895(which is not included in FIGS. 17, 18, and 19 in order to allow othercomponents to be visible). Drive gear 880 includes gear teeth (notshown) around its circumference 899, which engage drive shaft teeth 889.Drive gear 880 also includes a central circular opening 898. Surroundingopening 898 is an open cylinder 897. Circular flange 896 resides withinopening 898 and has an annular opening 898 a. Six holes 881 areuniformly dispersed around annular opening 898 a in flange 896. Bearing885 is fitted into annular opening 898 a.

Axle subassembly 894 includes axle 890; axle ring 893 and attachmentunit 892 are rigidly fixed to axle 890. Six vulcanized natural rubberpins 891 are fitted into six corresponding holes in axel ring 893, whichare uniformly dispersed about axel 890. As is shown, the rubber pinsextend parallel to axel 890. One side of the test head attaches toattachment unit 892 so that tumble rotation of the test head about theaxis defined by the rotational center line of axle 890 is provided.(This is the previously described “tumble” axis.) To minimize the torquerequired to rotate the test head about this axis, the axis may bearranged to pass approximately through the center of gravity of theload.

Axle 890 fits within bearing 885 and each rubber pin 891 fits into acorresponding hole 881 in flange 896. Bearing 885 may be mounted so thatit spaces axel ring 893 slightly apart from flange 896. Thus, axle 890,axle ring 893, and attachment unit 892 are flexibly coupled to drivegear 880. The rubber pins 891 are stiff enough so that if drive gear 880is rotated, axle subassembly 894 rotates with it, provided anyrotational load coupled to attachment unit 892 is not too great, as isthe case when the rotation axis passes through the approximate center ofgravity of the load. However, if drive gear 880 is rigidly held in afixed position, the rubber pins are flexible enough to allow a loadcoupled to attachment unit 892 to be rotated plus or minus a few degreesby a reasonably small external force. Spacing axle ring 892 apart fromflange 896 reduces the possibility of shearing rubber pins 891. Also,the relative stiffness of the assembly may be adjusted by varying thisspacing. Thus, the assembly provides a compliant rotational drivemechanism. In a manipulator system, this provides a desirable componentof compliant motion of the test head when docking with a peripheral.Thus, attachment unit 892 is capable of a limited amount of rotationalmovement with respect to drive gear 880 even when drive gear 880 isstationary. This is due to the flexibility of the rubber pins 891 whichcouple axle unit 893 to gear 880.

As shown in FIG. 21, drive gear and axle assembly 895 reside within well855 of tumble drive unit 800. Axle 890 is perpendicular to drive shaft830. The gear teeth on the circumference 899 on drive gear 880 engagecorresponding gears 889 (not shown) on drive shaft 830 so that rotationof drive shaft 830 causes rotation of gear 880 and, accordingly, drivegear and axel assembly 895 and the load attached to it. Appropriate geararrangements such as worm gears or spiral gears may be used so thatdrive gear 880 rotates about an axis that is orthogonal to the axis ofrotation of drive shaft 830.

Tumble drive housing 840 includes hole 841 (see FIG. 17) through whichaxle 890 passes. Cover 860 includes hole 861 (see FIGS. 17, 18 and 19)through which attachment unit 892 protrudes. Bearing members 865 areincluded to provide a precise, low-friction fit.

Tumble pivot unit 900, shown in FIGS. 22 a and b, is a non-poweredattachment unit that is attached to the other side of the test head.Tumble pivot unit 900 is attached to vernier arm 600. As previouslydiscussed, vernier arm 600 moves upwards and downwards along linearguide rail 570. Tumble pivot unit is essentially a rectangular box thatprovides a means of coupling to a pivotable test head mounting device.In an exemplary embodiment, this amounts to a hole 901 through the pivotunit. A stub axle (not shown), which passes through this hole 901 may bemounted to the test head. Appropriate bearings may be utilized toprovide low friction. Tumble pivot unit 900 and tumble drive unit 800(“tumble units”) are attached to their respective vertical vernier arms600, 700 by means of attachment screws (not shown) which engageattachment holes. This allows for simplified installation or change overof the test head. For example, to install a test head, one first removestumble pivot and drive units 900, 800 from the manipulator. These maynow be attached to the test head. Then the assembly of test head andtumble pivot and drive units may be conveniently attached to the testhead.

FIG. 23 is a perspective view of a docking mechanism in accordance withan exemplary embodiment of the present invention. Exemplary test head1000 is included in FIG. 23. Test head 1000 is coupled to bracket 1005.Bracket 1005, in turn, is coupled to tumble drive unit 800 and tumblepivot unit 900. A plurality of docking mechanisms 1010 are attached tothe sides of test head 1000. In this exemplary embodiment, three dockingmechanisms 1010 are shown. Each docking mechanism 1010 is situated onbottom support 1020. Docking mechanism 1010 is attached to sidecalibration bars 1015 via appropriate bolts or adjustment screws 1075.Side calibration bars 1015 are used for fixing docking mechanism 1010 tobottom support 1020. Bottom support 1020, in turn, is attached to bottomcalibration bars 1025. Bottom calibration bars 1025 are attached tobottom calibration platform 1030 via appropriate bolts or adjustmentscrews 1035. Thus, docking mechanism 1010 can be moved in an appropriateposition by changing the position of docking mechanism 1010 relative toside calibration bars 1015 and by changing the position of bottomsupport 1020 relative to bottom calibration platform 1030. Docking frame1050 is also shown. Docking frame 1050 is affixed to the peripheraldevice (that is, a device or package handler, a wafer prober, or othertest apparatus.). Affixed to docking frame 1050 are a plurality ofdocking pins 1060. Docking pins 1060 and docking mechanism 1010 arepositioned so that docking pins 1060 are aligned with and mate relativeto respective docking mechanisms 1010.

FIG. 24 is a perspective view of docking pin 1060 shown in FIG. 23.Docking pin 1060 includes docking pin base 1100 with pin sections 1150,1140 and 1130 extending there from. As shown, pin section diameters maybecome increasingly narrow approaching the tip of docking pin 1060. Thisis particularly useful when docking a test head with a peripheral devicebecause the smaller diameter of pin section 1130 relative to the otherpin sections allows for greater initial error when docking the test headwith the peripheral device. By giving the positioner system sufficientcompliance (i.e., minor unpowered movement) it is possible to correctfor minor misalignment between the test head and device handler when thedocking operation occurs. Also shown in FIG. 24 are cam followers 1120which extend from the sides of docking pin 1060. Cam followers 1120engage appropriate slots which are formed in docking mechanism 1010 andwhich will be described later.

A cut-away side view of an exemplary embodiment of the present inventionis shown with reference to FIGS. 25 a and b. Also, an explodedperspective is shown in FIG. 26. In FIGS. 25 a and b, docking pin 1060is shown after initial insertion into pin receptacle 1300. Docking pin1060, in FIGS. 25 a and b, is shown as already penetrating pin detector1400. Pin receptacle 1300 is coupled to arm 1600. Arm 1600 is moved as aresult of a piston included in piston unit 1500. Piston unit 1500includes piston 1515 and piston shaft 1510. Piston unit 1500 alsoincludes pivot points 1505 on opposite sides thereof (only one side isshown in the figures). Pivot points 1505 enable piston unit 1500 to havea small amount of pivotal motion. In an exemplary embodiment piston unitis a pneumatic unit; however, other types could be used such ashydraulic or electromechanical units. Pivot points 1505 enable pistonunit 1500 to pivot about pivot guides 1080 which are situated on thesides of enclosure 1012 and cover 1014 which face inward within dockingmechanism 1010. Arm unit 1600 includes pivot points 1620. By engagingpivot guides 1090 (again situated on the sides of enclosure 1012 andcover 1014 which face inward within docking mechanism 1010), Pivotpoints 1620 enable arm 1600 to have pivotal motion.

In FIG. 25, the piston 1515 within piston unit 1500 is more clearlyshown. The operation of the various features of pin receptacle 1300 isdescribed below.

FIG. 26 is an exploded perspective view of docking mechanism 1010. Inthis figure, it is possible to see docking mechanism enclosure 1012 aswell as docking mechanism cover 1014. Also there is shown pin receptacle1300, pin detector 1400, arm 1600 and piston unit 1500.

In FIG. 27, there is shown a perspective view of pin receptacle 1300.Pin receptacle 1300 includes cam grooves 1305. There is one cam groove1305 milled in each side piece 1315 of pin receptacle 1300. Camfollowers 1120 which are shown extending from the sides of docking pin1060 in FIG. 24 engage grooves 1305. Pin receptacle 1300 is slidinglyattached to enclosure 1012 and cover 1014. In particular bar 1316engages slot 1022 in enclosure 1012, and bar 1317 engages slot 1021 incover 1014. As will be further described, motion of piston 1515 andpiston shaft 1510 is coupled to pin receptacle 1300 by means of pivotingarm 1600. Thus, motion of piston 1515 causes pin receptacle 1300 toslide left and right. In the figures, pin receptacle 1300 will be in itsrightmost position when piston 1515 is furthest to the left so thatpiston shaft 1510 is retracted. Similarly, pin receptacle 1300 will bein its leftmost position when piston 1515 is furthest to the right sothat piston shaft 1510 is extended.

FIG. 28 is a perspective view of pin detector 1400. As shown, pindetector 1400 includes detector tab 1405. FIG. 29 shows pin detector1400 with detector tab 1405 removed. Detector switch 1410 is visible inFIG. 29.

FIG. 30 is a perspective view of detector tab 1405. Detector tab 1405includes tab opening 1450 about which detector tab 1405 is able topivot. Detector tab 1405 includes roller mechanism 1470 which is held inplace via an axel inserted through roller opening 1460. Detector tab1405 includes rear member 1480.

Operation of pin detector 1400 is shown more clearly with reference toFIG. 103 b. Specifically, as docking pin 1060 enters pin detector 1400,detector tab 1405 is pushed backwards as it pivots about tab opening1450. As a result of pivoting backwards, rear member 1480 pushes againstdetector switch 1410. In this way, pin detector 1400 signals thatdocking pin 1060 has entered pin detector 1400. Detector switch 1410 maybe an electrical switch in an electrically controlled system, air valvein an all pneumatic system, or, more generally a valve in any fluidbased system.

FIG. 31 is a perspective view of piston unit 1500. Piston unit 1500includes piston 1515 (not visible), piston shaft 1510, and arm mount1520.

FIG. 32 is a perspective view of arm 1600. Arm 1600 includes arm body1630. Arm head 1610 is attached to one end of arm body 1630 via headpivot 1660. This allows head 1610 to have pivotal movement. Extensions1640 are attached to the opposite end of arm 1630. Extensions 1640include extension openings 1650, respectively. Arm pivot 1620 is alsoincluded.

As shown in FIG. 33, docking pin 1060 is in position relative to dockingmechanism 1010 so that docking may be accomplished. At this stage ofdocking, docking pin 1060 is situated above the opening to cam grooves1305 in pin receptacle 1300, which is in its rightmost position. Also,as there is nothing that is pushing detector tab 1405 toward detectorswitch 1410, pin detector 1400 is indicating that pin 1060 has not beeninserted. More generally, the test head has been maneuvered to aposition by a positioner, such as positioner 10, such that, firstly, alldocking pins 1060 are aligned as indicated by FIG. 33 with respect totheir respective docking mechanisms 1010 and, secondly, the dockingsurface of test head 10 and the surface defined by docking plate 1050attached to the device peripheral are approximately parallel. The testhead is then said to be in a “ready-to-dock” position. The encodersincorporated in positioner 10 enable this position for a specificperipheral device to be recorded by the system controller. Thus, thesystem controller may automatically position the test head to aready-to-dock position that it has previously learned.

As shown in FIG. 34, docking pin 1060 has now been moved into dockingmechanism 1010 to a “ready-to-actuate” position. In particular, camfollowers 1120 have entered cam grooves 1305 to a position where theymay be captured by the downward sloping region of cam groove 1305 shouldpin receptacle 1300 be slid to the left. Also, docking pin 1060 is farenough into docking mechanism 1010 so that docking pin 1060 is nowpushing against detector tab 1405. The components are arranged so thatwhen docking pin 1060 has reached this position, it will push againstdetector tab 1405 sufficiently to enable rear member 1480 to pushagainst and activate switch 1410. Once switch 1410 has been thus pushedinward, docking mechanism 1010 may be actuated. More specifically, thecomponents are arranged so that switch 1410 becomes activated when theready-to-actuate position is achieved.

More generally, during docking, the test head is urged from aready-to-dock position to a ready-to-actuate position where all dockingpins 1060 are in the ready-to-actuate position with respect to theirrespective docking mechanisms 1010. Thus, when all detector switches1410 have been activated, all docking mechanisms 1010 are simultaneouslyactuated. Preferably, none of the docking mechanisms 1010 are actuateduntil all detector switches 1410 have been activated.

In moving between the ready-to-dock and ready-to-actuate positions thetest head, as is well known, is preferably moved along a straight paththat is orthogonal to the plane of docking or docking frame 1050 inorder to protect the delicate electrical contacts that are to beengaged. In an automated positioner system such as described herein, thesystem controller has the responsibility to provide such controlledmotion. The system controller may record the ready-to-actuate positionfor the specific peripheral device from the encoders and use thatinformation to control this action.

In an exemplary system, the ready-to-dock and ready-to-actuatepositions, as well as other positions, may be input to the systemcontroller by a teaching procedure. In the teaching procedure, the testhead is put into the various positions by an operator manually operatingthe positioner. At each position, the system is commanded to read theencoders and record the coordinate values. A series of such “learned”positions may later be used by the system to describe a path to befollowed. Thus, the system controller may automatically move the testhead along a path from a service position (i.e. a position at which thetest head is serviced), away from the peripheral device, to aready-to-dock position, and then to a ready-to-actuate position.

It is important to note at the stage of the docking process, where thetest head is in the ready-to-actuate position, that power to thepositioner system drive motors is suspended. However, pressure to thepneumatic cylinders 440, 540 and any other powered devices included toprovide compliant motion must be maintained. More specifically, as thepositioner system moves the test head into various positions, thepositioner system is aware of the location of the test head by virtue ofa number of position encoders, which have been previously described.Thus, when the position encoders in the positioner system indicate thatthe ready-to-actuate position has been achieved, the various motorsincluded with the positioner system now stop all further poweredmovement. Further motion of the test head will be provided by dockingmechanisms 1010. If any of the manipulator motors are equipped withbrakes, they are released in order to allow compliant motion of the testhead. Now that the position shown in FIG. 34 has been achieved, dockingmechanism 1010 is now in a “ready to actuate” mode. In this mode,instead of the positioner system continuing to push the test head towardthe peripheral device, docking mechanisms 1010 will now pull the testhead towards the peripheral device. In an exemplary embodiment of thepresent invention, docking mechanism 1010 is actuated by air pressureand may begin this pulling sequence just prior to the positioner systemreleasing its motors. Thus, control signals between the docking systemand the positioner system are not needed to coordinate this phase ofdocking.

FIG. 35 illustrates docking mechanism 1010 after the actuation processhas started. In other words, when docking mechanism 1010 is in the stateshown in FIG. 35, docking mechanism 1010 is now in the process ofpulling the test head towards the device handler. More specifically, thefollowing events occur. As all detector switches 1410 have now beendepressed, piston unit 1500 is activated, and piston shaft 1510 withinpiston unit 1500 now begins to extend. In an exemplary system, pistonunit 1500 is pneumatic and is activated by applying air pressure. Aspiston shaft 1510 extends, arm 1600 now begins to rotate about arm pivot1620. As arm 1600 rotates about arm pivot 1620, head 1610 pushes pinreceptacle 1300 so that pin receptacle 1300 now begins to slide. Becausearm 1600 is pivoting, head 1610 will move in an arc as it pushes pinreceptacle 1300. Thus, head 1610 rotates slightly relative to arm 1600as arm 1600 pivots. Space is provided for the vertical component of thearc motion of head 1610. In FIG. 35, it is seen that pin receptacle 1300has slid towards the left relative to its position in FIG. 34. As pinreceptacle 1300 slides, cam groove 1305 slides relative to cam follower1120. As is noted in FIG. 35, cam groove 1305 has increasing depth fromits opening to its end. Thus, as pin receptacle 1300 is moving, pin 1060is pulled downwards as a result of the sliding motion of pin receptacle1300.

FIG. 36 illustrates docking mechanism 1010 in the fully docked position.In this position, piston shaft 1510 has extended enough, and arm 1600has pivoted enough, so that pin 1060 has been pulled sufficientlydownward so that the test head and peripheral device are now docked.

As the test head is pulled from the ready-to-actuate position to thefully docked position, relatively small motions in all six degrees ofspatial freedom are made as the docking pins pull it into precisealignment with the peripheral device. Thus, the positioner systempreferably allows compliant motion in its motion axes. In positionersystem 10 this is provided by de-energizing and releasing brakes on allmotors except the vertical drive motor 330. This action combined withthe compliant effects derived from pneumatic cylinders 440 and 540 andtumble drive unit 800 provides the desired compliance. Alternatively,should these means not be sufficient, other known and previouslydisclosed approaches may be readily incorporated.

When it is time for the test head to be undocked relative to the devicehandler, piston 1510 can be signaled to retract so that arm 1600 pivotsclockwise and groove member 1120 is situated at the opening of groove1305. When this has been achieved, further separation of the test headfrom the device handler may be accomplished by energizing the motorswithin the test head positioner system.

A control system may be used to control the positioner system. Thiscontrol system (hereafter, the “positioner's control system”) may be amicroprocessor based system to control the various components (e.g.motors, pneumatics, etc.) of the positioner system. An additionalcontrol system for docking mechanism 1010 (hereafter, the “dock'scontrol system”) may also be microprocessor based. An overall sequenceof operations for docking an exemplary test head with an exemplaryperipheral device is as follows:

-   -   1. An operator manually “teaches” the positioner's control        system the locations of the ready-to-dock and ready-to-actuate        positions for the particular peripheral device.    -   2. The operator also “teaches” the positioner's control system        the service position and a sequence of any relevant points along        the desired path between the service position and ready-to-dock        position.    -   3. The test head is placed in the service position and prepared        for testing.    -   4. On command the positioner's control system automatically        causes the test head to be positioned to the ready-to-dock        position as determined by its encoders.    -   5. On reaching the ready-to-dock position, the positioner's        control system may provide a signal to “turn on” or enable a        separate dock control mechanism, described further in steps 8        and 9 (see FIG. 37, Step 5).    -   6. The positioner's control system now carefully moves the test        head along a straight line path orthogonal to the docking plane        to the ready-to-actuate position as determined by its encoders        (See FIG. 37, Step 6). Brakes for motion not related to the        straight line path maybe applied.    -   7. After a time T, the positioner's control system de-energizes        its drive motors and releases the brakes (if they were applied)        on any motor so equipped, except for the vertical drive motor.    -   8. Within time T, the dock's control system recognizes that a        test head is in the ready to actuate position by noting that all        switches 1410 have been activated.    -   9. Following step 8 and still within time T, the dock's control        system actuates all piston units (further driving unit) 1010        (see FIG. 37, Step 9).    -   10. When time T expires, the test head is moved under the        control of the dock control system to the fully docked position        while the positioner allows compliant motion in all of its axes        (see FIG. 37, Step 10).    -   11. Now that respective electrical contacts on the test head and        the peripheral are mated, testing between the test head and the        peripheral may take place. At the user's preference the motor        brakes may be energized to lock the positioner in place, or they        may be left unlocked to allow vibrations to be absorbed.

Although the invention is illustrated and described herein withreference to specific embodiments, the invention is not intended to belimited to the details shown. Rather, various modifications may be madein the details within the scope and range of equivalents of the claimsand without departing from the invention.

1. Apparatus for supporting a load, comprising: a plurality of columns;a plurality of main arms moveable along said columns, respectively, formoving said load along a first axis; at least one vernier arm moveablealong at least one of said main arms, said vernier arm providingcompliance about a second axis orthogonal to said first axis. 2.Apparatus according to claim 1, further comprising a pneumatic unit forallowing movement of said vernier arm.
 3. Apparatus according to claim1, further comprising a coupler coupled to a side of said load, saidcoupler moveable with said vernier arm, said coupler moves said loadalong said first axis and about said second axis.
 4. Apparatus forsupporting a load according to claim 2, further comprising a swing platefor moving said load about said first axis.
 5. Apparatus for supportinga load according to claim 3, wherein when said load moves about saidsecond axis, said one of said couplers moves in one direction whileeither: a) another of said couplers moves in an opposite direction; orb) another of said couplers remains stationary.
 6. Apparatus forsupporting a load according to claim 2, further comprising an in-outplate, for moving said load along said second axis.
 7. Apparatus forsupporting a load according to claim 2, further comprising a side toside plate for moving said load along a third axis orthogonal to saidsecond axis.
 8. Apparatus for supporting a load according to claim 2,wherein said coupler rotates said load about a third axis orthogonal tosaid first and second axes.